Fluid drive mechanism



|- J. MURRAY FLUID DRIVE MECHANISM Filed OGt. 25, 1940 U. @om om @om @om u. @om n mm oww no; m n 1 e /I L/ V mm m V VW mv m .o l.. mq @m www f mw@ 15m mm .Q x wm mv l nm an, Sw: @j mm @Q x mv Q el.- lm Oml /Ilf m mi m nm m @mW m@ mmwm w mm Wm mum HM H////\\\\\\\ u: Imm. .Mlmml mm. mm mm m Km m vm Immunrml .WNW mw E mm @m um. Hw. mw f// w\\\\\\\\\\\ mm Jun uw om mmm m m |h|| |l| @m N\v\\\\\ mm mm\ \\MN\ vm 0C @Nm mm @i m @l @om v Patented Oct. 9, 1945 UNITED STATES 'PATENT OFFICE FLUID DRIVE 'MECHANISM Howard J. Murray, New York, N. Y.

Application October 25, 1940, Serial No. 362,777

Claims. (Cl. 74,18 9. 5

The present invention relates in general to an automatic iiuid drive power transmission mechanism, and specifically relates to a device for automatically changing the fluid drive action of the fluid drive coupling of the said mechanism in accordance with the drive resistance of the driven member of the said mechanism.

One of the objects of the present invention is to provide a normally positive drive clutch arranged to automatically become a fluid drive clutch in accordance with the torque load on the driven member of the said clutch.

A further object of the present invention is to provide a simple form of uid drive mechanism arranged with cam controlled fluid drive elements actuated by power derived from one of the power members of the said mechanism.

A still further object of the present invention is to provide a combination ofcam vdrive connected uid drive elements arranged so as to be-` come uid drive related in accordance with the torque load resistance on the driven element.

The present invention is a further development of the disclosure included in my U. S. patent application No. 358,062 filed September 24, 1940 entitled Fluid drive mechanism.

While the present invention is obviously capable of use in any location wherein it is desired to transmit power from one power member to another power member, the present invention is obviously applicable to a power transmission device for use in connection with automotive vehicle construction, and it is in this connection that embodiments of the present invention will be described in detail.

Accordingly the present disclosure includes. torque responsive fluid drive elements for effecting positive drive and uiddrive relations in 'a selective manner during periods of varying torque load on the driven velement without shock or strain.

In one embodiment of the present disclosure a plurality of normally inactive uid drive elements are cam related so as to become torque responsive thereby to accumulatively become iuid drive related with fluid drive intensity varying faster than the load increase on the driven member.

In the drawing:

Figure 1 is an embodiment of the present invention partly in vertical section taken axially of the main shaft.

Figure 2 is another embodiment of the present invention partly in vertical section taken axially of the main shaft.

Figure 3 is a plan view of a section of the means of Figure" 1 taken along the line 3--3 looking in the directioiiiri'clicated by the arrows and showing the 'normalrelatinn ofthe cammed elements. Figureii 4sl'io'vers-fth'e cammed' elements of Figure 3 in an"oprativ"'position and the relative position of the' cams.

Figure 5 is a plan view of a section of the means f Figure `2 taken alongthe line 5 5 of Figure 2 looking inthe direction indicated by the arrows. 'f Y l Figure 6'is` another view' of 1 the means of'Fig'- ure 5 showing thecammed elements and asso# ciated portions of the means of Figure 2 in torque responsive 'operated relation.4 j

4Figure '7 is a diagrammatic presentation of the varies-of thei'uid drive'elements of Figures 2, 5 andtshowingthe normally inoperative relation of the s aid vanes. d

Figures is a diagrammatic presentation ofthe elexiic-ln'ts of 'Figure 'lshowing the torque responsive 'operative relation of thevanes of Figure 7.

'I 'here is shown by the means of Figure 1 of the drawing anew and `novel self-controlled uid drive mechanism including a pair of power shafts I0 'and T I disposed in axial alignment with their adjacent ends including the reduced portion 48 of the 's haft H interiitted to provide proper bearing surface, K The power shafts Ill and Il are normally drive related so that the said shafts have independent rotary movement respectfullyv in suitable bearings 2and 2l Asupported in the casings I8 and 2 9. r While either of' the shafts I0 and Il may be` considered as the normal driving member of them'echanism, it will be understood for the purpose of this description that the shaft ID is the normal`dr'iving member, and is operatively conncted' so"as to be driven from a source of power (not shown) such as an internal combustion engine. 4 Y

Accordingly the said shafts Ill and Il arenormally drive related so that the shaft ll is the driven member, and is operatively connected to whatever mechanism (not shown) it is desired -to drive. Y

The shaft; I0 is preferably made of a good quality of steel and formed with a radially extending anged portion 36 and axially extending annular portions 34 and 63 together forming an axially extending recessl 35.

'Iwo 'uid drive elements 26 and 21 (see Figure l) formed with fluid fins 30 and 3| are supported and axially positioned on the drive and driven power members `lll 'and'll for rotation DU. VUVV U1 VLAN l5- bBaI'Cn therewith as hereinafter described. The fluid drive element 21 is securely attached to the portion 32 of the normally driven member II by means of the axially extending portion I1. Any conventional securing means such as the screws 62 may be used. The fluid drive element 26 is formed with the axially extending portion I6. This portion I6 is securely attached to a plurality of axially extending portions I symmetrically positioned about the axiscof the member I0 so as to collectively have a limited vdegree of rotational freedom` on the portion 63 of the member I0 (see Figures 3 and 4). This degree is determined by the relation of the radial walls 25 and 65 as shown by the numerals indicating the spaces B3 and 55. Thus the uid drive element 26 basa degree of rotational freedom relative to the normally driving member I Il snch'freemn's eliminated by the action of a torque load impressed on the normally driven member "I I as hereinafter described.

A-n .axialiy movable cammed member 21--c is formed with a plurality of axially extending cammed projections 28 --extending in mating recesses 39 formed in the portion `32 of the'member II land' positioned and slidably supported on the axially extending portion 63 of the .member I0. This 'cammed member -Z'I-c has a limited degree of axial movement` as determined by the mating cams 28 and 39 so that the member portions 21-c and 32 will relatively move so as to bring the cam surfaces'28 Aand -39 opposite each other as shown by Figure 4 along the axially extending guide wall 33 rof the member I0. A spring 25 with preferably a tapering cross-section is positioned in the annular recess -35 so as to normally hold the cammedmember 21c in the inoperative position .shown ,by Figure 3. 'I'he cammed member 21--c is .formed with a second cammed portion`52 to operatively mate when .axially moved with thecammed portion 50 of the rotatablylimited tsee space 53) member 5.I vas shown JW Figure-4.

The casings i8 and 29 are secured together by means of the bolts 38 Kand va conventional gasket so` as to .form a leak-proof container for the rotatable .elements of Figure 1. The end pieces .23 and 24 are lsecured to the castings I8 and 29 by means of the bolts 22 so that the .fluid drive .couple members 26 andfl .will-be spaced apart as indicatedby thenumeral ail-a. The said end pieces 23 and 24 aretormed so as to receive and position the .duid retainers 31 as shown by .Figure l. .The casing portion I8 formed wtha bell-housingporticn I8 operatively attached .to .the vehicle upon which `the device is to be installed and operated.

By meansof Figurez there is shown a modification of themeans of Figure 1 which employs more than two' :Huid drive elements. In -this embodiment four uid drive elements with duid drive vanes -d,. 3ll j,.30-g andJO-aare arrangedas .shown .in Figures A2,. and 7 so that the vanes SII-g end 3D-Pf are normally uid drive inactive. to .aoonsiderable degree as hereirrafter described. The webs 30-d, 30-gand 30-f are operatively -connected with the member lvI Il. andthe vanes 3B-e turn with the member II Yas hereinafter described.

lnepower members Il-a 'and IvI--a are intertted by meanscf thebearing Portion Aso as to be disposed` in :axial alignment. Themembcrs 4IIJ-aa and II-a are mounted Afor independent rotary movement .respectfuliy in SwitahJebearinUs 2 205mm 32| in turn positionedmd i in' o supported by the casings I B-a and 29a secured together so as to form a uid enclosure by means of the bolts i-a.'

While either of the power members III--a and I I-a may be considered as the driving member of the means of Figure 2, for the purpose of this description, it will be understood that the member III-a. is the driving member, and is operatively connected to be driven from a source of power (not shown) such as an internal combustion engine. 'I'he conventional automotive vehicle clutch may be operatively placed between Ithe source of power and the member IU-a if desired.

AAccordingly the member II-a is regarded as thedriven member, and is operatively connected to Whatever mechanism (not shown) it is desired to drive.

The members IO-a and II-a are preferably made oi a good quality of steel, and the shaft II-a isformed with a plurality of splines or sun teeth I2 so as to operatively receive the planet teeth of a plurality of sets of planet gears I3-a and III-a constantly in mesh drive relation with the annular teeth of the annular gears I4-b and IS-b. The member IIi--a is formed with a. radially extending portion I3-b in bearing relation with an axially extending portion of the annular gear i4-b.

The planetary arrangement of the sun, planet and-annular teeth of the annular gears of Figure 2 is similar to the annular arrangement of the sun, planet and annular teeth of the gears of Figure 1 of my co-pending U. S. application Serial No. 358,062 filed Sept. 24, 1940.

The fluid drive elements 2Ba and 21a of Figure 2 are preferably moulded or cast with the inner walls IB-a and I'I-a securely attached for rotation with their supporting annular gear members -I-4b and I5-b by such conventional means-as screws or bolts, or by a forced nt. The present disclosure contemplates that the uid drive ele-ment 26-a (or 2`I-b) may be moulded of plastic material with the vanes 30-d and the walls Ni--a and 26-a integral.

The fluid drive elements are preferably made of Welded sheet metal of proper thickness-so that the inner rims 4I, 4Ia and outer rims 40 and 40d and the webs 30g and 3U-f may be welded together. Thus the rims 40 and 4I and the webs S-g will constitute one fluid drive element, and the rims 40-a and 4I-a andthe webs 30-f will constitute va second fluid drive element. 'Ihe viiui'd drive element 4i! is rigidly secured to the cammed portion 60 (see Figures 5 and 6) -including the closed annular ring portion vt5. The cammed portionti `('see Figures -5 7and 6) including the closed annular portion 416 isrigidly secured to the fluid drive element 4IJ-a. Thus the inner band4-I portion of the drive element 40 is secured to the cammed element 60, and the ring 4I-a is secured to the cammed portion 6I.

The cammed portions 60 and 6I are normally heid inthe mating position shown by Figure 5 due tothe action of the cam seating springs 43 and "44 positioned in the annular recesses 42 formed'in the outer portions of the annular gears I 4b and I5b. The springs 43 and 44 press against the closed ring portions 45 and `46 to hold the cams and vlfl in the position shown in Figure'.

After the said duid drive elements 2li-a, 2'I-a, 40 and'MI--a including the vanes SI1-cl, 30-g, SB-f and 39-e are operatively assembled on the annular gears I4-b and `IE--b, the power c l n members IO-a and II-a are positioned in the bearings 2li and' 2| and the casings I8-a and 29--a are bolted together by means of the bolts 38-a. After the container formed by the casings I8-al and 29-a is properly llled with the selected fluid the end members 23 and 24 are bolted to the casings by means of the bolts 22 after the iluid retaining material 31 is in proper position.

The member l-a may be attached to the source of power as th bell housing portion I9-a is moved into position for proper support on the vehicle to which the device is to be installed and operated.

In operation, let it be assumed that the source of motive power (not shown) is connected to the normally driving member I of Figure 1. Let it be further assumed for the purpose of this description, that the said source of power will rotate the said member I0 clockwise as viewed from the left hand end of the means of Figure 1.

The device to be driven, such as an automotive vehicle, is assumed to be connected to the normally driven member II through a conventional reversing unit (not shown) and that the normally driven member I I is normally driven in the same rotational direction as the normally driving member I6.

The transmission casing including the portions I8 and 29 is assumed to be properly lled with a suitable uid for both uid driving and for lubricating the various movable portions within the said casings. One of the novelties of the present disclosure is that of providing a fluid drive power transmission mechanism in which the uid drive medium may also be used to lubricate the movable parts employed in the said mechanism as well as to transmit power.

With the said normally driving member I0 rotating clockwise at constant speed (assumed as constant speed for the purpose of this description only, as of course the member I0 may rotate at variable speed) and without any appreciable impressed load torque on the normally driven member I I, all of the rotatable parts of the means of Figure 1 (except the bearings 2|) and 2|) will tend to rotate as a unit at the said constant speed about a common axis.

Now let it be assumed that a slight load torque is impressed on the normally driven member II. The said member |I will then normally tend to decrease slightly in its clockwise speed relative to the driving member I0. But the seating spring 26 is holding the mating cammed portions 28 and 39 of the cammed members 21-c and 32 (see Figure 3) in the mating position shown by Figures 1 and 3 and thus the slight torque load resistance impressed on the normally driven member |I will not be suicient to axially move the cammed portion 28 of the 'cammed member 21--c to the left to compress the spring 26 so as to permit the camming portions 28 and 39 to move relative to each other with a limited degree of axial and rotary movement. Thus the member will remain in positive drive relation with the normal driving member I0. Now let it be assumed that the impressed torque load on the driven member II is further increased until the connecting force resolving action on the means of Figure 1 will be sufficient to overcone the axial force of the seating spring 26 to cause the camming portions 28 and `39 to move relative to each other to the left and thus compress the said spring 26. It is obvious that the means of Figure 1 will continue` to transmit power from the member I0 to the member |I at conventional direct drive conditions until the normal impressed load torque on the member II has been exceeded to move the cam portions 28 and 38 relative to each other to compress the spring 26. In this eveni-l there will be no fluid drive action between the elements 26 and 21 of Figure l as long as the normal impressed load torque on the member I I is not exceeded.

Now let it be assumed that the impressed load torque on the driven member Il is sufcient to overcome the axial resistance of the spring 26 and thus cause the cammed member 21-c to moxe axially to the left as shown by Figure 4.

The cammed axial projection 28 of the member 21-c will be moved axially to the left away from the recessed cammed portions 39 of the portion 32 to compress the spring 26 against its tension.

As soon as the uid driving vanes 30 and 3| move relatively to each other there will exist a ow in the uid medium and thus a fluid drive action between the said vanes 30 and 3|. The segmental portions 5| are collectively rigidly connected to the inner rim I6 of the fluid drive element 26 as hereinbefore described, and the fluid drive element 26 and associated portions thereby have a limited degree of rotational freedom relative to the driving member I 0. Thus any iluid drive action by the vanes 38 will react to cause the member 26 to rotate relatively counterclockwise to the member l0. In this event, the segmental portionsl attached to the uid drive member 26 will tend to rotatably move against the cammed portion 21-c. (see Figure 3). As the cammed portions 21 and 39 approach the maximum axial displacement position as shown by Figure 4, and before such a maximum displacementl position is reached by the cammed portion 21 of the member 21-c, the cam surfaces 52 of the cammed portions 21 of the member 21--e will have been axially moved to the left suiicient to be in the path of the cammed surface 64 sufciently to cause the now torque actuated surface 64 to cam engage with the surface 52.

The reaction between the vanes 30 and 3| will be transmitted to the portion 5| to rotate it in the space 53 formed in the member Ill to cause the cammed portion 50 to force the cammed portion surface 52 to the left toward the stop wall 34 (see Figure 1). Thus the cammed surfaces 64 and 52 will react under the rotational torque force of the member to axially move the cammed member 21-c to the left until it reaches the stop wall 34 as the member 5| moves to the stop wall 25 (see Figures 3 and 4). Thus the member 21-c will be moved into the locked position as shown by Figure 4. 'I'he axially movable cammed member 21-c is thus moved entirely out of the path of the mating cammed member 5I to permit the member 5I and the uid drive element 26 to be moved into the operative position as shown by Figure 4. Under these conditions the cammed projections 28 have been moved axially with the member 21-c so as to be entirely out of the path of the cammed portion 32 of the normally driven member, and the means of Figure 1 thus become fluid drive related in turn to iluid drive relate the power members I0 and II. The members I0 and II-will continue to remain fluid drive related as long as the said impressed torque load on the member l I is greater than the normal torque load as herinbefore stated.

When this greater than normal torque load decreases to below normal, or to a value where the spring 26 can push the-cammed segmental .fuiven I'LANIB.

portions 2`|-c axially to the right in Figure 1, the portions .5| will be rotated clockwise (as viewed from the left hand end of the means of Figure 1 to the position as shown in Figure 3). The cammed projections 28 of the member 21-0 will move into the mating recesses in the portion 32 of the normally driven member and the mechanism of Figures 1 and 3 will again be in positive drive relation.

The mechanism shown by Figures 1, 3 and 4 is therefore torque responsive, and the power to operate the cams and to automatically change the mechanism from one form of drive to the other is derived from the driving member. All of the transmitted power will pass through the positive paths as shown by Figure 1 when the cammed members 21-c and 32 are in the positions shown, and through a differential fluid path when the cams are in the position shown by Figure 4.

When the normally driven member becomes the driving member, the cam action between the cammed elementsIT-c and 32 of Figure 1 will be the same as when the member is the driving member, but the fluid drive action between the vanes 3|! and 3| will tend to move the vanes 30 and thus the cammed portion 5| relatively clockwise faster than the said member ||l until Cross Heterenct stopped by the wall portion 65. In this event the cammed portion 64 of member 21--c will not act to lock the cams 28 free from the member 32, because the uid drive relations between the webs 30 and 3| when the web 3| is driving will be to move the web 30 clockwise faster than the member I0 of Figure 2.

It should be noted that the iiuid drive relation must always take place when the impressed load on the driven member is greater than normal torque load. Most of the time, the device will be operating at normal torque or less and thus there will be no molecular friction loss in the uid medium because there will be no uid drive action. In most automotive vehicles, direct drive relations hold for a greater portion of the operating intervals, and thus the present disclosure provided a highly efficient positive drive mechanism automatically becoming a fluid drive mechanism when required. The cammed member 21-c is torque responsive in its axial movement to automatically cause the rotatable means of Figure 1 to selectively become a positive drive or a fluid drive means according to the torque load on the driven member.

By means of Figure 2 there is shown a combination of means using more than two uid drive elements. In this combination of means, the iuid drive elements 2lia and 21-a are not connected directly to the driving and driven members as shown of the means of Figure l, but are drive related to the said members through planetary gearing so as to be differentially drive related to either member.

rIhe fluid drive elements 40 and l0-a are cam connected to eheh other, and the element 40 is drive connected. to the member |4-b with a limited degree c; axial movement as hereinafter described. The fluid drive element 40--a has a limited degree of rotational freedom relative to the fluid drive element 4I), and both fluid drive elements 40 and lll-a have a limited degree of axial freedomrof movement relative to each other.

In the operation of the means of Figure 2, let it be assumed that the normal driving member |0-a is rotating clockwise at constant speed as viewed from the left hand end of the means of 588mb l aeeaase Figure 2. If there is no appreciable impressed load torque on the normally driven member ||a there will be no appreciable force resolving action between the rotatable parts of the means of Figure 2. All the said rotatable parts will rotate clockwise as a unit at the same speed about the common axis of the members |0-a and II-a.

If a slight load torque is now impressed on the driven member II-a, the connecting force resolving action between the constantly mesh drive connected sun, planet and annular gears will vary accordingly as the speed of the driven member tends to decrease clockwise relative to the speed of the driving member. Suflicient impressed load torque on the member ||a will cause a difference of speed between the said members |0-a and ll-a and thus a difference of speed between the fluid drive elements 26a and 21-a depending on the differential speed drive relation of the said sun, planet and annular gears.

As long as there is no relative movement between the cammed members 6|) and 6|, the fluid drive elements 40 and 40-a will rotate with and at the speed of the uid drive element 2E-a. Initially the uid drive action between the elements 2lia and 21-a will not be effective, because of the fluid vane arrangement of the fluid drive elements ZB-a, 40, lw--a and 21-a as shown by Figure 7. 'I'he spaces 30-b and 30-c are so wide as to initially decrease the fluid flow from the vanes 3Ud by permitting a partial short circuiting of the said fluid flow between the vanes 30-d and 30-g and 3|l f. Furthermore, the vanes 30-d and 30-g and 3|i-f are initially rotating at theifspeed of the driving member Ill-a. The fluid flow from the iiuid drive elements 30-g and 30-f will also tend to become short-circuited in the openings 30-b and 3||c so that very little of the iinid flow and thereby very little power will be transmitted from member 26-a to 21-a.

In order to maintain the planetary relations of the sun, planet and annular gears it is obvious that a decrease in speed of the member ||a (with member |0--a rotating at constant speed) will necessarily cause a clockwise increase in speed of the annular gears |4--b and |5-b. Because of the cascade differential arrangement of the gears of Figure 2, the clockwise speed of the annular gear |5-b will increase faster than the clockwise speed of the annular gear |4-b. Thus the difference in speed of the vanes 30-d and 30-e will increase with decrease in speed of the member ||-a. With proper design the difference in speed between the vanes 30-d and 30-e may increase faster than the decrease in speed of the member I-a.

'I'he partially short-circuited fluid drive action between the elements 2lia and 21-a will be increased with increase of torque load onthe member ll-a. The fluid drive actions of the vanes 3IJ-g and 30-f will depend 4entirely on the relations of the cammed portions 60 and 6|. If the torque acting on the vanes 30-g and 38-f is sufficient to move the cammed portions 60 and 6| relative to each other an accumulative and progressive drive control action will be initiated by the means of Figure 2. The cammed member 6| and thereby the vanes 30-f will rotate relative to the cammed member 60 and the iins 30-g. 'Ihe movement will tend to compress the seating springs 4.2 and 43 to move the cammed member 60 and thus the fluid drive element 40 axially to the left along the splines 58 (see Figures and 6) formed on the annular gear I4-b to receive the mating recess 51 formed on the member including the closed ring portion 45 and the cammed portion 60. Thus the vanes 30-g will move axially to the left as the vanes 3D-f move obliquely against the spring 43 to the positions shown by Figure 8.

The uid drive element 40 includes the vane portions 30--g, cammed portion BIJ, closed ring portion 45, and inner ring portion 4I. The fluid drive element 40-a includes the vane portions 30-1, cammed portion 6I, closed ring portion 46, and inner ring portion 4I-a.

Any relative movement of the vanes 30-g and 30-f from the positions shown by Figure 7 to the positions shown by Figure 8 will cause an increase of iiuid drive action between the members 26--a and Z'I-a., and in the same manner, any increase in the iiuid drive action between the members 2li-a and ZI-a will vary the relative movement of the vanes 30-g and 30--f.

An increase in fluid drive action of the vanes 30-g and 30-f will increase the reaction between the cammed portions lil)V and 6I and the compression of the seating springs 43 and 44. Such action will cause further relative movement between the vanes 30-g and 30-f. The openings 3Il-b and 3ll-c will decrease and thus any short-circuiting of fluid ow action will decrease as the vanes 30--g move axially and the vanes 30-f move obliquely to the positions shown by Figure 8. The fluid drive action between the vanes 30-d and 30--e will be intensified in an accumulative manner by power accumulatively derived from the driving member lll-a. The fluid drive elements of Figure 2 are self-energizing to control the speed drive relations of the members IIJ--a and II-a as a function of the torque load on the driven member.

The cams 6l) and 6| and the seating springs 43 and 44 may be provided so as to desirably limit the self-energizing action. The spring resistance to the camming acti\n may vary in intensity faster than the increase' of the relative movement between the cammed members 60 and 6|. 'Ihe uid drive elements of Figure 2 are torque responsive to react on the planetary gearing to create connecting torque converting action between the sun, planet and annular gears and therethrough the members Ill-a and lla.

The means of the modication shown by Figure 2 provide an automatic self-energizing uid drive control mechanism varying in control intensity in accordance with the torque load on the driven member, or varying in accordance with some predetermined action of the cams 60 and 6| and the springs 43 and 44. For example, the springs 43 and 44 may be formed so as to present a tapering resistance.

A portion of the power transmitted from the member Ill-a to the member II-a will always be transmitted through the plurality of positive toothed power transmitting paths provided by the sun, planet and annular gears of the means of Figure 2. The fluid drive elements collectively act as a fluid control in accordance with the load torque on the driven member to vary the power absorbed or shunted through the fluid path.

This is true, because the fluid drive elements as hereinbefore described act as a self-energizing frictionless brake varying in the intensity of its holding (control) action in accordance with the dierence in speed of the said driving and driven members to control the transmission of power through the various paths collectively provided by the differential gearing. The maximum flow control action will occur when the vane portions of the said uid' drive elements are in the relation as shown by Figure 8.

Now let it be assumed that the torque load on the driven member lI-a is decreased. 'Ihe relative clockwise speeds of the annular gears |4-b and IS-b and thus the relative clockwise speeds of the fluid drive elements 26-a and 2'l-a will decrease. This is true, because normally the speed of the member ll-a will increase as its load is decreased. The fluid ow reaction between the elements 26a and Z'l-a will decrease, and the torque pressure holding the springs 43 and 44 will decrease. With suilcient decrease of impressed torque load on the member H-a the compressed springs 43 and 44 will return the cammed members 60 and 6| and thus the vanes 30-g and BIJ-f to the positions shown by Figure 7.

The springs may be formed so that thecams 60 and 6| cannot pass each other. The cammed members 60 and 6I may be stopped by the compressed springs 43 and 44 so that the cam 6| cannot reach the position as shown in Figure 6. Ifthe means of Figure 2 are adjusted so that the cams 60 and 6l may pass each other, then the torque resolving action of the means of Figure 2 will be self-limiting because the reactions between the cammed members 60 and 6l cannot exceed that required to cause the said cams to overrun each other.

The arrangement of means as shown by the modification of Figure 2 will co-act to produce a comparatively large starting torque on the member II-a, because the uid drive action of the fluid drive elements reach a maximum drive action with the normally driven member II-a at rest. This is true, because the annular gears |4b and l5-b will reach the maximum clockwise speeds with the member ll-a at rest. The maximum diierence of speed of the uid drive members 26-a and 21a will occur when the member H-a is at rest. Therefore, the maximum fluid drive action, and the greatest dinerential force resolving action of the annular gears will occur to tend to move the member lI-a.

When the normally driven member H-a becomes the driving member, the rotatable elements of Figure 2 will all rotate clockwise as a unit at the same speed about a common axis as long as no appreciable torque load is impressed on the now driven member lll-(1. With sumcient load impressed on the now driven member IIJ-a its clockwise speed will normally decrease. The annular gears I4b and I5-b will now decrease in clockwise speed. The annular gear lS-b will decrease in clockwise speed faster than the gear I4-b. Further increase of lmpressed torque load on the member Ill-a will cause the annular gears |'4-b and IS-b to continue to decrease in clockwise speed, but the difference in speed of the gears |4--b and |5--b and thus the fluid drive action of the fluid drive elements will increase. The torque reactions oi the dilerential gearing will increase to the extent that the cammed members 60 and 6| will be moved relative to each other to tend to move the uid drive vanes 3ll-d, 30-g, 30-f and 3ll-e into the uid drive relations as shown by Figure 8.

As the clockwise speed of the membersv |4-b and IS-b continues,V the members will pass through zero speed and thence rotatev counterclockwise one after'the other.

This vane moving action will be progressive and accumulative because the uid movi-ngV action of.the vanes 30-g and 3iJ-f'will increase as the said vanes 38-g and 3-e are moved into aline with the vane 30e-d. This increase in ilniddrive intensity will cause further cam action between the cammed members 66 and 6| to further increase the web moving action and so on.

With'properV design the collective fluid' drive action of the vanes SULd', SI1-g and 36-1 operativeiy constituting one of the fluid drive elements of aiiuid 4drive couple, the uid drive action ofy the means-of-Figure 2-may be controlled so as to increase in intensity as a function oi' the increase of impressed load torque on the member driven.

The seating springs 43- and 44 maybe provided` so as to produce resistance against compression varying faster orv slower than the axial movemerrtof the cammed members 60* and 6l. In any event a predetermined action between the springs, Cairns,V annular gearsr'and uid drive elcmerrts may be obtained.

If' the load torque on the member I'-a is' now decreased thel connecting force resolving action ott-the means of Figure 2 will decrease; The speed of the now driven member W-a will normally increase (the speed of the-now driving-member Il-a-remaining-constant as hereinbeforestated) 'Ihe uid drive action between the vanes-ofthe duid drive elementsl 2G-'a, 4U, #0 0 and 2T"-awi11 decrease. The springs 43-and 44" will tend to move the cammedmembers- Eiland EI-axially-to the position shownbv Figures 2 and 5. With suillcient load decrease on the member llr-a'the springs #5a-nd 44 will be able to movethe cammed members andtheassociated vanes to the posit1ons-sliowrr byy Figures- 2., 5 and '7; 'Ihe uid drive action between the members` 2B-a and' Zelf-a will again'be reduced toa minimum and the molecular friction loss' inthe" uid medium Wilrbe reduced to a minimum.

Iiil conclusion, it willbe understood that' the' present disclosure provides cammed luid drive control means for progressively and' accumulatively effecting drive relations between a driving member and a driven member at different speedtorque' ratios; The self-energizing action can be variedor limited relative to the torque load imposedI on-the-driven member. The power for op eratine the cams and cammed members is also derived from the driving member as a function o'ti'ie load torque impressedv on the driven member. A duidv drive controlmeansV (see Figure 2i is-provided by this disclosure whereby fluid pressures are progressively and accumulatively produced and employed in a static and/or kinetic manner so as-to cause-force with torque responsive varying mechanicaladvantage to permitone" member to speed drive another member accordingMv toltlie load torque on the said driven member;

Whiler l2 have shown rndb have described andz pointed out in the annexed claims certain newL and novel features of my invention, it will be understood that certain Well known equivalents of the elements illustrated may be used, and that various other substitutes, omissions and changes in the form and details of the devices. illustrated andin their operation may be made by those skilled in the art without departing. from the spirit of myinvention.

HavingV thus described my invention, I' claim:

Cross Heierence search tessa, ac*

1. In-aaself-energizingdrive controldevice, the combinationl of; a driving rotor, adrivenrotor;l a fluid and a fluid drive means inv drive relation; said means including eascadedl planetary gearing sets'a fluid coupling element drivecormected'ttr one of the rotorsthrough one of the saidset's; a second fluid drive elementdrive connected to the other rotor through another of the said-sets', aA third fluid drivev element and' a fourth uiddrive element formed so asl to be resiliently camdrive connected to eachl other, said third and' said fourth drive elementsw fluid drive related to the said second fluid drive element; said cam drive connections fluid controlled for causingtheA said third and fourth HuidV drive elements to move axially relativeto each votherin accordance with the differencev in speedof the 'said rotors as they are rotatedrelativi-aA to each other to col-operatet'o. vary the uid drive' action ofall the sai'd'elements- 2; The combinationof'dnve and driven rotors and drive related drive-control means, saidcon.- trol means including a'iluid; cascaded planetary gearing sets, a rst iiuid drive element drive com. nected to one of the saidisets, a second Huid drive. element drive connected; to-another of the said sets, and associated torque responsive andud responsive uid'drive elements, said fluid' responsive elements mounted for rotation with the saidl second'elementfor a limited degree of relative m tary and resilient axial movement' to each other so as to vary the uiddrive relation of all thesaid elements of the said control andtherethrougli tha drive relation ofthe saidjrotors.

3. In a i'ui'ddrive control organization.. the. combination'oi a pair' or rotors and a uid drive` i control means in diirerential drive relation. about 'elements to vary the duid a common axis; saidA organization.Y including. a. uiddriveelement gear drive related tov one, or the rotors, a'uid drive element positively drive. related to the other rotor and further fluid drive elements each provided'with an element of a cam,- said cam elements co-operatin'g accord? ing to theA diilerence inspeedof the saidrotors to vary theuid drive relation, ofthe said rotors:

4'. In a. drive control, the combination. of a pair ofrotors and a fluid drive control in drive relation, said control-including'` fluid drive elements in drive relation'with the rotors,. and further cammed uid' drive'elements, said further fluid elements operatively positioned between thesaid rotor drive related elements, said furtherv elementscam actuated relative to each other and mounted for rotation by one ofthe said fluid drive elements so as to' vary their axial and. rotative relation" to each' other and to the said drive related elements, resilient means positioned. hetween the said' drive' relate-di elements. and the said further elements and cao-operating with the cammed portions' ofthe said further, drive relation in aocordance'with the diierence in speed' of the said' rotors, said actuation varying' the intensity of the duid drive action, of" the said. control. in accordance with the said'difference in speed.

5; 'I'he combination of.' a driving member., a` driven member'and' a drive related fluid drive. control' means operatively positioned' therebetween; said means including a fluid and two associated'fluididrive'members in fluid'drive relation with each other andindiierential'drive relation with the said drive and driven members, a plural'ity of' resilientl;r c'amnl'edfil' drive elmet's. in cam'drve relation' with' each other, one ofsaid" cammed'fiuidl elements :in'drive relation with one' of the saidA fluid' drive members, said cam drive relation varying according to the difference in speed of the said members.

6. In a gear control, the combination of driving and driven sun, planet and annular gears in differential drive relation, a iiuid and fluid drive elements fluid drive related to each other, certain of the said elements positively drive related to the said annular gears, certain other of the said fluid drive elements provided with torque controlled camming means, said camming means mounted on one of the said annular gears so as to have a limited degree of movement relative to each other and to the said annular gear thereby fluid drive relate all the said fluid drive elements according to the diilerence in speed of the said annular gears.

'7. In an automatic power transmission, the combination of a pair of rotors in drive relation, a fluid, and fluid drive means differentially drive connected to the said rotors and fluid drive related to a limited degree, and further fluid drive means cam drive connected to each other and drive connected to one of the said differentially connected fluid drive means, said cams operatively responsive to a difference in speed of portions of the said differentially drive connected means to cause the uid drive means to become fluid drive active to a greater degree in a progressive manner in accordance with the torque load on one of the said rotors.

8. In a power transmission mechanism, the combination of a pair of rotors, cascaded planetary gearing and a fluid drive control in differential drive relation, said control including certain impeller and runner fluid drive elements positively gear drive connected to the said rotors through the said gearing, and further fluid drive elements mounted for rotation with the said impeller element cam drive related to each other and fluid drive related to the said certain iuid drive elements, said further elements axially positioned relatively to each other and to the said runner and said impeller as a function of the dilerence in speed of the said rotors.

9. In a uid drive device, the combination of a pair of rotors, a iiuid and gear drive related fluid drive means, said means including uid drive impeller and runner elements in gear drive relation with the rotors, and further uid drive elements formed with operatively associated camming portions, resilient means axially positioned between the said impeller and runner portions and the said cam portions, said cammed portions controlled by the relative speed of the said rotors for varying the fluid drive action of the said impeller, runner and further element means, said further uid drive elements mounted for rotation with the said impeller element.

10. In a liuid drive, the combination of a pair of rotors mounted for relative rotation, a uid drive control including impeller and runner uid drive elements for causing the said rotors to normally tend to rotate at the same speed, said control including further uid drive elements, said further elements formed with operatively associated resilient cams arranged for moving the said further elements relative to each other with two modes of motion, said cams mounted for rotation with the said impeller and controlled by the relative speed of the said rotors for causing the uid control to begin to function.

11. In a uid control for power transmission mechanism including a driving member, a driven member, a fluid medium, cascaded planetary gearing, a uid drive element drive related to the said driving member through the said gearing, another fluid drive element drive related to the said driven member and further fluid drive elements each formed with an element of a cam, said cam elements mounted for rotation with one of the said uid drive elements so as to be operatively associated by power derived from one of the members through the said fluid according to the difference in speed of the said members thereby to control the uid drive relations of all the said fluid drive elements.

l2. In a device of the class described, a fluid, a driving member, a driven member, and a fluid drive control meanstherebetween, said control means including cascaded planetary gearing, a rst fluid drive element drive related to the driving member through one of the cascade sets, a second fluid drive element drive related to the driven member through a second cascade set, and further uid drive elements formed so as to be resiliently cam drive related and fluid operated by the said fluid according to the diierence in speed of the said members, said further elements mounted for a limited degree of relative axial movement between the said rst and second elements and drive related to an element of one of the said cascaded sets.

13. In a device of the class described, the combination including a driving member, a driven member, a fluid medium, and a fluid drive control means in differential drive relation, said control means including an impeller element in drive relation with the said driving member, a runner element in drive relation with the said driven member and two fluid drive elements operatively positioned between the said impeller and said runner and mounted for rotation with the said impeller, said two elements formed with camming portions actuated by power derived from the driving member according to the dilerence in speed of the said members, said camming acting to move the said two elements with two modes of motion relative to each other.

14. In a device of the class described, the combination including a driving member, a driven member and a uid drive control mechanism operatively positioned therebetween, said mechanism including an impeller element drive related to the said driving member, a runner element drive related to the said driven member, two uid drive elements mounted on the said impeller element for rotation therewith, said two elements formed with cammed portions, and resilient means for causing the said portions to be moved relative to each other with two modes of motion as the portions are rotated with the said runner in the mechanism fluid.

l5. In a device of the class described, the combination including a driving member, a driver member, a fluid medium and a fluid drive contro` mechanism in diierential gear drive relation ir the said fluid, said mechanism including an impeller element in gear drive relation with th driving member, a runner element in gear drivi relation w'th the said driven member, a pluralit: of cammed fluid drive elements mounted fo: rotation with the said runner element, sail mounting arranged so that the said cammed ele ments are operatively associated as the said run ner is rotated in the said medium, said associa tion causing relative movement of the sail cammed elements in two planes, and resilien means positioned so as to tend to oppose suc] relative movement.

HOWARD J. MURRAY. 

